Transmission with gear groups connected in tandem arrangement



Oct. 2, 1956 T.F.K TRANSMISSION WITH GEAR MMICH IN TANDEM ARRANGEMENT GROUPS CONNECTED Filled Feb. 12. 1952 United States Patent O TRANSMISSION WITH GEAR GROUPS CON- NECTED IN TANDEM ARRANGEMENT Theodor F. Kmmich, deceased, late of Stuttgart, Germany, by Maria K. Kmmich, administratrix, Stuttgart, Germany, assignor to Daimler-Benz Aktiengesellschaft, Stuttgart-Unterturkheim, Germany Application February 12, 1952, Serial No. 271,212 Claims priority, application Germany February 12, 1951 Claims. (Cl. 74-763) The present invention relates to a transmission, preferably for motor vehicles with gear groups particularly designed as planetary gears connected in tandem arrangement, wherein main one-way clutches and reverse oneway clutches are used for transferring or sustaining the torque while changing over from one transmission ratio or speed gear to another.

An object of the present invention is especially the application of the principle of one-way clutches and reverse one-way clutches also for such gears with gear groups connected in tandem arrangement. In the former patent application, Serial No. 234,075, by Hans-Joachim M, Foerster, led June 28, 1951, and entitled Change Speed Gear and Method of Shifting Therefor, a connection was produced, for example, by appropriately arranging main one-way and reverse one-way clutches adapted to be connected to and disconnected with multiple speed gears so that, when changing over from one to another transmission ratio or speed gear, for example, from a lower to a higher speed or gear, rst an intermediate stage or intermediate state was established, in which, with the engine driving the output shaft, the previously engaged speed or gear was kept on, whereas the new speed or gear was engaged with the output shaft driving the engine, e. g. with vehicles driving downhill and/ or when the throttle of the engine is relieved, so that a drive was effected in either direction of drive in the newly engaged speed or gear only when at least one further clutch was engaged. In this way it was possible to change from one to another speed gear by steps without interrupting the drive, particularly Vso that the above-mentioned intermediate stage was engaged .by disengaging a clutch or` a brake corresponding to the clutch, and then thenew speed gear was definitely engaged by connecting another clutch or a brake corresponding to the clutch. However, the application of this principle met with difficulties for gear groups in which one must shift alternately in a rst gear group and in a second gear group. p According to an important characteristic of the present invention these ditliculties, particularly when using planetary gears, are eliminated by providing in addition to the driving connection normally serving for the transmission of torque from the tirst to the second gear group, another supporting connection by way of a one-way clutch betweengear members of both gear groups particularly between brakable gear members of the twoplanetary gears. Moreover, according to a further characteristic of the present invention in addition to this one-way clutch an additional reverse one-way clutch is provided for between the gear member of the two gear groups so that, when changing over from fthe one to the other gear group with a drive in one direction of drive, for example, with the engine driving the output shaft, the one one-way clutch takes up the drive, and with a drive in the other direction of drive, for example with a pushing vehicle when the output shaft drives the engine, the reverse one-way clutch takes up the drive. V Y

More particularly, according to another characteristic Patented Oct. 2, 1956 of the present invention, the arrangement of the transmission is made in such a way that each of the two planetary gears produces a drive transmission by braking a gear member thereof, preferably the rst planetary gear pro- .acing a gearing up, and second planetary gear producing a gearing down, and by the engaging two gear members together thereby producing a direct drive transmission; for this case a one-way clutch is coordinated with the brakes 0r clutches, the One-way clutch coordinated with the brake of the second planetary gear being supported on the brakable gear member of the first planetary gear. The one-way clutch in the additional supporting connection isl expediently adapted to be disengaged by an appropriate 'clutching arrangement. The engagement of this supporting connection is only necessary when a changing over from the one to the other gear group, particularly a planetary gear, is required; however it is appropriate to effect engagement thereof ahead of time, at a moment when there exists no difference in speed between the parts to be clutched, particularly when these parts are inactive.

Owing to the present invention it is also possible to utilize with group gears the advantages given by using one-way clutches and reverse one-way clutches, namely to avoid an interruption of the drive during the shifting, particularly at any position of the throttle valve lever of the engine. More particularly, in this case, too, with every change over from a lower to a higher speed gear or reversely, an intermediate stage or an intermediate state may be established, in which, depending on which of the two coordinating` one-way clutches takes effect, a higher or a lower speed gear picks up the drive. It is a further advantage of this mode of shifting that the clutches must not be matched as to the clutching operation and the clutching pressure, as they are engaged temporarily one after another in any intervals. According to a further characteristic of the present invention, by changing over from the one to the other gear group, an intermediate stage being provided for, in which, when changing up temporarily into a higher than the next speed gear, for example, into the 4th instead of the 3rd, with the output shaft driving the engine it is possible t0 restrict to a single shifting operation the more complicated mode of shifting on account of the operation of several clutches, which is otherwise required when changing over from the one to another gear group.

Iffurthermore care is taken that the one or the other clutch is engaged in a shifting state of the transmission, at which the parts to be clutched are in no difference of speed with respect to one another or the clutch is inactive, it is a further advantage that the concerned clutches may be designed small, and because of the non-existing centrifugal forces without releasing springs.

Further objects and advantages of the present invention will become obvious from the following description when taken in connection with the accompanying drawing which shows for purposes of illustration only one embodiment in accordance with the present invention, Iand where- 1n:

Figure 1 is a schematic diagram of the transmission in accordance with the present invention;

Figure 2 is a cross sectional view of the one-way olutchfi;

Figure 3 is a cross sectional view of the one-way clutch f2;

Figure 4 is a cross sectional view of the one-way clutches f3 and f4; and

Figure 5 is a cross section illustrating the construction :of the transmission in accordance with the present invention schematically illustrated in Figure 1.

Referring now more particularly to the drawing where like reference characters are used in the various views thereof to designate lileep'arts, reference character a indicates the transmission shaft drivenV by the engine, for example, by way of a main clutch, b the output shaft driving, for example, the driving axle of a motor vehicle, between whichthe planetary gears P1 and Paarek inserted in tandem arrangement -as group gears. The firstp'lanetary gear P1 consists of the planet carrier r comprising the planet pinions s and connected with the transmission shaft a, furthermore of the sun gear `t and the ring. gear u; the second planetary gear P2 consists of the snngear v connected with the ring gear u by means ofthe intermediate shaft c, the double planetary gears w1, wz, supported on the planet carrier x, and the sun gear y connected with the transmission shaftl b. Y

The sun gear t of the first planetary gear is, on the one hand, brakable by a brake P1' whereby the planetary gear P1 gears up from a to c, and, on the other hand, adapted to be clutched with the ring gear zt by a clutch q1 in order to get a direct transmission in the planetary gear P1. Furthermore, the sun gear t is supported on the case by a one-way brake including one-way clutch f1 and releasable brake p0 inserted between the case and one-way clutch f1 and adapted to be disengaged, so that the one-way brake with an engaged brake po allows a rotation of the sun gear t in the main direction' of the drive of the shafts a and b, i. e. in the direction of arrow z (Fig. 2). Moreover, there is `another one-way clutch f3 inserted between the transmission shaft a and the intermediate shaft c (Fig. 4) so that this one-way ciutch allows an overrunning of the intermediate shaft c with respect to the shaft 1, yet blocks a reverse relative movement. Another one-way clutch f4. (Fig. 4) is disposed between the intermediate shaft c, andby inserting a clutch qo--the planet carrier x of the second planetary gear P2 so that it allows an overru'nning of the intermediate shaft c in the direction of arrow z with respect to the planet carrier x, yet blocks a reverse relative movement.

Moreover, the planet carrier x is, on the one hand, brakable against the case by -a releasable brake p2 whereby a gearing down of the planetary gear P2 from c to b is effected, and, on the other hand, clutchable with the drive shaft b by means of the planetary gear P2 for obtaining a direct transmission.

According to the presen-t invention, the planet carrier x of the second planetary gear is furthermore connected on the sun gear t of the first planetary gear by way of a clutch qa, 'a hollow shaft d, and a one-way clutch f2 so that, as illustrated in Fig. 3, the one-way clutch f2 allows an overrunning of the hollow shaft d, and of the planet carrier x with respect to the sun gear t, yet blocks a reverse relative movement.

The transmission operates in the following way: In neutral position all thc clutches and` braltesare disengaged.

1st speed germ-Clutch q1 in the planetary gear P1 and the brake p2 in the planetary gear Pz are engaged. Simultaneously, e. g. when starting the vehicle, caused by a uid pressure produced by a pump driven by the output shaft, the brake po and the clutch qo may be engaged and they remain engaged in all forward speed gears. (Accordingly, these particular shifting operations lare no more mentioned hereinafter.) The planetary gear P1 is blocked by the clutch q1 and thus it transmits directly, whereas the planetary gear P2 acts as an intermediate gear v, w1, wz, y, and gears. down due to the braking of the planetary carrier x by the brake p2.

Intermediate stata- For engaging the second speed gear first the clutch q1 is designated. With the engine driving the output shaft, due to the resistance at u, the sun gear t tends to overrun the planet carrier r in the direction z, which is allowed by the one-way clutches f1 and f2 (qs being disengaged), yet is prevented by the one-way clutch fs, so that the shafts aand c are coupled with each other, and keep on the direct transmission in the planetary gear P1. Thus the irst speedgear remains engaged when the engine drives the output shaft, the onepway clutch f3 functioning as the clutch q1 for this direction. of drive.

With the output shaft driving the engine there is nothing changed in the speed ratio of the planetary gear P2 whereas in the first planetary gear P1 the sun gear t tends to move backward (opposite to"z)1,-due to the drive of u and the resistance of r. However this is preventedV by the one-way clutch f1, acting'as aV reverse one-way clutch. As a result of it t is blocked, and r or a is driven with a lower speed than c, which is allowed by the one-way clutch f3. Thus the transmission ratio obtainedv in the' planetary gear P1 corresponds to a gearingup from a toc, and for the entire transmission to a transmission in the second speed or gear.

2nd speed germ-For definitelyV engaging the 2nd speed gear the clutch p1 is engaged. It thereby functionsv as the reverse of .one-way clutch fraud constitutes a brake for sun gear t in either direction of the drive so that the sun gear t is also blocked when the engine drives. In this way the planetary gear P1 gearsup, the planetary gear P2 gears down, the effect of entire gear system is to gear down, too. With tas well as x beingV blocked, i. e. remaining stationary, the clutch qamay be engaged during the second speed gear along with p1 since the parts x and d to be engaged by engagement ofclutch q; are not moving relatively to each other. Thereafter the clutch qs may remain engaged in Iall the following speedV gears.

Intermediate stage-First brake p2 is disengaged, i. e. released, while p1 as well asqg remain engaged.` In this way the transmission in the planetary gear P1 Vremains the same as in the second speedgear, i. e. agearing up from a to c, whereas inthe planetary gear P2 the following conditions occur: With the engine'driving the output shaft, owing to the resistance at y, the sun gear v tends to drive the planet carrier x in the backward direction of rota tion, i. e., opposite to the direction of arrow z. However, this is prevented by thc-one-way clutch fz by means of which the hollow shaft d connected with x supports itself on the sun gear I blocked by p1 so that thesecond speed gear remains engaged.

With the output shaft driving.V theengine, owing to the resistance at v and the drive at y, the planet carrier .r is shifted forward with respect to shaft c, i. e. attempts to rotate in the direction z with respect thereto, which is allowed by the one-way clutch f2, but prevented by the reversal one-way clutch f4. In this way the planetary gear Pz., rotates as; a wholeV in direct gearV whereas the planetary gear P1 gears up from a to c. On the whole this means a temporary engagement of the 4th or overdrive speedv or gear with the output shaft driving' the engine.

3rd speed gaan-inonder to definitely engage the 3rd speed gear, brake p, is released and thereupon first the clutch q and then the clutchY q2 is engagedlnthis way the planetary gear Pr as well as the planetary gear Pz are blocked in themselves so that a direct clutching is effected between the shafts a and b by way of the transmission.

late/mediate stage-in changing over to the 4th gear the same shifting operation is followed as in changing over from the lst to the 2nd speed gear. Thus first the clutch q, is disengaged again. Accordingly, with the engine driving the output shaft, due to the resistance at u, the shaft a and the sun gear t tend to overrun the intermediate shaft c which is however prevented, on the one hand, by one-wayV clutch f3 and, `on the other hand, by one-way clutch f2 as shaft d rotates with the same spec as shaft c due to the blocking of the planetary gearPz. Consequently the direct speed gear remains engaged, as Pz also provides a direct transmission ratio. Y

With a pushing vehicle, i. e. the output shaft driving the engine, due to the drive at 1,.' and the resistance at r, the sun gear t tends to run backward, which is prevented by one-way clutch f1. Therefore the gearing of P1 corresponds to the overdrive speed so that with a pushing vehicle the entire overdrive speed transmission is engaged.

4th speed gear (overdrive gear) .-In order to definitely engage the 4th speed gear p1 is engaged. In this way t 6 a first power transmission line connecting a second of the three members of the iirst planetary gear with one of the three members of the second planetary gear, a transmission member driven by a second of the three is blocked in either direction of drive, so that, with the 5 members of the second planetary gear, a second power' engine driving the output'shaft as well as with a pushtransmission line connecting the third of the three meming vehicle, i. e., the output shaft driving the engine, P1 bers of the first planetary gear with the third of three brings about a gearing up, and P2 a direct transmission. members of the second planetary gear, said second In this way the overdrive gear is engaged definitely. power transmission line containing a one-way clutch and The changing down in gears or speeds is done in a 10 an interrupting clutch, irst means for varying the eleccorresponding reverse way. tive transmission ratio of the iirst planetary gear, and

The changing may be effected in any way, for example, Second means for varying the eiective transmission ratio mechanically, hydraulically, pneumatically, electrically or 0f the Second planetary gear. in any other way. However a fixed order must be fol- 2. A transmission comprising a iirst planetary gear lowed in changing. The reverse speed may be established with three elements including a planet carrier supportin any way. For instance a two speed gear alternately ing at least one planet pinion and two central gear wheels changing over from forward to reverse speed gear may in engagement with said planet pinion, a second planetary be superposed to the group gear or arranged behind it. gear also with three elements including planet carrier Figure 5 illustrates a construction of the transmission supporting at least one planet pinion and two central according to Figure 1. In this case the shifting of the gear wheels in engagement with said second-named planet brakes and clutches is eiected hydraulically in the above pinion, a member driving one of said three elements of described order. The brake p0 and the clutch q0 are dethe first planetary gear, a iirst power transmission line signed as piston-shaped cone clutches, whose pressure connecting a second of said three elements of the rst space is supplied by a pump driven by the output shaft b. planetary gear with one of said three elements of the The brake p1 is designed as a single disk clutch controlled 25 second planetary gear, a transmission member driven by by the pressure space ki. The clutch q, is designed as a second of said three elements of the second planetary a double cone clutch, which is engaged by a spring i1 gear, a second power transmission line connecting the and disengaged by a hydraulic pressure in the space k2. third of said three elements of the iirst planetary The functioning of the clutch q2 which is exposed to gear with the third of said three elements of the second the action of a spring for disengagement thereof, and planetary gear, said second power transmission line conwhich is engaged by the pressure in the space k3, is cortaining a one-way clutch and an interrupting clutch, responding. The brake p2 is designed as a multiple disk first means for Varying the eective transmission ratio Clutch which is engaged by a Spring is, and which is disof the first planetary gear, and second means for varying engaged by hydraulic PrcSSnrc acting n the Pressure the effective transmission ratio of the second planetary space k4. The clutch q3 is designed as a cone clutch, 35 gean and is engaged by the pressure in the pressure space -its. 3. A transmission according to claim 2, wherein in The engagement bem? eeected Wlth maeeve elutchfng said iirst planetary gear said one of the three elements is parte a Separate elutehmg spuug may be dlepensed with' said planet carrier supporting at least one planet pinion,

Further details of the transmisslon shown 1n Figure 5 th d d th th. d d may be obtained by reference to Figures l through 4 40 e eeeee e. Img gear en e 1r .e sun geel. en wherein like parts are designated by like reference char- Wherem m. Sele Second planetary gear Sele one of the three acters and which show some of the elements of the transelemelts 1S a Sun gear thc Second also a .Sun gear and mission of Figure 5 in detail. In order to facilitate underthe thlrd Sad secondfn'amed Planetary Carnet Suppomng standing of the operation of the transmission shown in at least one Planet Pmlon Figure 5, reference may be had to the following chart 4- A transmission according to claim 2 further Colnwhich indicates the status of the various parts of the prsing another one-Way clutch acting inversely with retransmission for the various speeds: spect to said first-mentioned one way clutch and pro- Releasable brake Releasable clutch One-way clutch Engine driv- Output shaft ing output driving shaft engine Po 111 172v qu q1 i12 12 f1 f2 fs f4 1st Speed eng-" diseng... eng. eng.-- eng diseng... diseng ggtdmm l-zntermediate eng dlseng... eng eng-" disengm diseng diseugm 0*) Saleeetas lst' 2dspeed. 2d Speed engi-- eng. eng---. eng-" diseng diseng eng glgggwn 2-3 Intermediate eng eng disengm eng--- diseng. diseng eng Saslgges 2d I 4th speed. 3d Speed eng-.- diseng.-. diseng.- eng--- eng.1st cng.2d eng 3-4 Intermediate eng--- diseng," diseng eng--- digttig. engeng C) Sasllles 3d l 4th speed.

tassa@ *Operative with engine driving output shaft.

Operative with output shaft driving engine.

What is claimed is: videdV for between said rst and said second power trans- 1. A transmission comprising a tirst planetary gear mission line. s comprising three members consisting of atleast one planet 5. A transmission according to claim 2 in which in pinion rotatably supported by a planet carrier and two said iirst planetary gear said planetcarrier supporting. central gear wheels in engagement with the planet at least one planet pinion is the first mentioned of the pinion, a second planetary gear comprising three memthree elements, a ring gear said-second mentioned elebers consisting of at least one planet pinion rota'tably ment, and a sun gear the third mentioned element, and supported by a planet carrier, and two central gear wheels in which in the second planetary gear a sun gear is said in engagement with the'planet pinion, a member actuone of the three elements, a further sun lgear the second ating one of the three membersof the iirst planetary gear, and said secondfmentioned planet carrier supporting at leastone planet pinion the third,.fur.ther comprisingy another one-way clutch acting inversely with respect. to said first one-way clutch and provided between.said.first power transmission line and the planet carrier of said second planetary gear.

6. A transmission according to claim 2, wherein said means for varying the-effective ratio of said firstY planetary gear comprises a brake adaptedV to block the third element of saidfirst planetary gear, and wherein said means for varying the effective transmission ratio of said ser.- ond planetary gear comprises a brake adapted to block the planet carrier of the third element of said secondmentioned planetary gear.

7. Av transmission according to claim 2, in which said rst means comprises a brake for the third element of said first planetary gear, and said secondmeans comprises a brake for the planet carrier. of said third element of said second planetary gear, and the planetary gears are formed so that in applyingv one of said brakes the coordinated. planetary gear gears up, and in 'applying the other of said brakes the coordinated planetary gear gears down.

8. A transmission according to claim 2, in which one of said two planetary gears comprises pairs of planet pinions connected together, and the two central gear wheels of said one planetary gear are two sun gears.

9. A transmission according to claim 2, in which said first means and said secondmeans comprise clutches and brakes, and hydraulic means, for controlling said clutches and brakes.

l0. A transmission according to claim 2, in which said rst means and said second means comprise clutches and brakes with resilient means for engaging the clutches and the brakes, and with hydraulic means for disengaging them.

ll. ,A transmission according to claim 2, in which said first and second means comprise blocking means for simultaneously blocking the elements connected with said second power transmission line, and wherein the clutch in said second power transmission line is designed as a cone clutch adapted to be engaged with the above-men` tionedy elements blocked simultaneously.

112. A transmission comprising a reiatively xed part, a -first planetary -gear with three members consisting of at least one planet pinion rotatably supported by a planetary carrier, and of. two central gear wheels, a second planetar` gear with. three members consisting of at least one planet pinionrotatably supported by a planet carrier with two central wheels, a driving membery being .in a driving connection land of one of the three members of the -first planetary gear, a power transmission .line connecting a second of these three members of .said first planetary gear with a first of lthe three members of said second planetary gear, a driven member being in a driving connection with a second of said last-mentioned three members, a brake for the third member of said first plane- .tary gear, a 4first clutch for locking said first planetary gear in itself, a releasable brake including a first oneway clutch between the lthird member of said first planetary gear and said relatively fixed part, enabling ia drive of said last-mentioned third member in only one direction of rotation, a second brake for the pla-net carrier of the third member of said second planetary gear, a second lclutch for locking said second planetary gear in itself, a 4second power transmission line between the third of the three members of said' first and the third of the three members of said second planetary gear containing a third clutch, and a second one-way clutch enabling a drive of the -third member of said first planetary gear with an inactive second power transmission line but in a direction of rotation reverse to said first one-way clutch, a third one-way clutch between said driving member and said lfirst power transmission line, and a fourth one-way clutch between said first power transmission and said second power transmission line enablingy a relative rotation of said tirstpower transmission linewith respectA to said driving member in the same rotation as with respect to said secondpowertransmission line.

i3.. Atransmission according -toclaim l2, in which said second. one. way clutch allows rotation of said second power. transmission line relative to the .third member of said first planetary gea-r in a reverse direct-ion4 of rotation, in thesame way 'as said lfourth one way clutch allows rotation of. said second power transmission line with respect to said first power transmission line.

i4. A transmission according to claim l2, in which the rst member of said first planetary gear lis the planet pinion snpported by the planetary carrier of said first planetary gear, andthe third, gear member of the second planetary is the. planet pinion supported by the planet carrier of said second planetary gear.

l5. A transmission according to claim l2, in which said fourth one-way clutch, 4is connected with said secondv power transmission line by means of the third member of said second planetary gear, and a fourth clutch between said fourth one-way clutch andthe third member of said second planetary gear.

16. A transmission according to claim 12, in which said fourth one-way clutch is connected with said second power transmission line by means of the third member of said second planetary gear, further comprising a fourth clutch between said fourth one-way clutch and the third member of said second planetary gear, and means for producing a pressure for operating saidv releasable brake and fourth clutch dependent on the driving speed of the driving member so that the said brake and clutch are kept engaged when exceeding a certain speed.

`17'. A transmission comprising a first planetary gear comprising three members consisting of at least one planet pinion supported by a planet carrier and two central gear wheels in engagement with theV planet pinions, a second planetary gear comprising three members consisting of at least one planet pinion supported by a planet carrier and two central gear wheels in engagement with `the planet pinion thereof, a member driving one of the three members of said rst planetary gear, a power transmission line connecting the second of the three members of said first planetary gear with one ofthe three members of said second planetary gear, a member driven by a second of the three members of said second planetary gear, another power transmission line connecting the third of the three members of .said first planet-ary gear with the third of the three members of said second planetary gear, speedV gear changing means each consisting of a clutch in each of the planet-ary gears for blocking each planetary gear in itself land one brake in each of the planetary gears for blocking that member which is connected to said second power transmission line, each clutch and brake includ-ing one-way clutch means coordinated therewith for producingupon engagement of said speed gear changing means by engaging and disengaging said clutches and brakes, first an intermediate stage, in which an immediately following speed may be engaged in one direct-ion of drive only between the driving member and the driven one, whereas the hitherto existing speed remains in the opposite direction of drive, and the new speed is engageable in either direction of drive by engaging only another speed of said speed gear changing means.

18. A transmission comprisingl a relatively fixed part, a first planetary gear with three membersconsisting of at least one planet pinion rotatably supported by a planetary carrier and of two central gears, a second planetary gear with three members consisting of at least one planet pinion rotatably supported by a planet carrier and of two central gears, a driving member drivingly connected with one of the three members of said first planetary gear, a power transmission line connecting a second one of the three members of said first planetary gear with a first one of the three members of said secondV planetary gear,

a driven member drivingly connected with a second one of the three members of said second planetary gear, a brake for the third member of said first planetary gear, a first clutch for locking said first planetary gear in itself, a one-way brake between the third member of said first planetary gear and sa-id relatively fixed part to enable a drive of said last-mentioned third member in only one direction of rotation, a second clutch for locking said second planetary gear in itself, a second power transmission line including a third clutch between the third one of the three members of said first planetary gear and the third one of the three members of said second planetary gear, and a one-way clutch intermediate said first power transmission line and said driving member to enable a drive of the first member of said second planetary gear in only one direction of rotation with respect to the first member of said rst planetary gear.

`19. A transmission comprising a relatively fixed part, a first planetary gear with three members consisting of at yleast one planet pinion rotatably supported by a planetary carrier and of two central gears, a second planetary gear with three members consisting of at least one planet pinion rotatably supported by a planet carrier and of two central gears, a driving member drivingly connected with one of the three members of said first planetary gear, a power transmission line including a first clutch connecting a second one of the three members of said first planetary gear with a first one of the three members of said second planetary gear, a driven member drivingly connected with a second one of the three members of said second planetary gear, a first bnake for the second member of said first planetary gear, a second clutch operative on the third member of said first planetary gear for locking said first planetary gear in itself, a one-way brake between the second member of said first planetary gear and said relatively fixed part to enable a drive of said last-mentioned second member in only one direction of rotation, a third clutch for locking s'aid second planetary gear in itself, a second brake for the first member of said second planetary gear, and a second power transmission line including a one-way clutch intermediate the first member of said first planetary gear and said second power transmission line for connecting the third member of said second planetary gear with the first member of said first planetary gear.

20. A transmission comprising a relatively fixed part, a first planetary gear with three members consisting of at least one planet pinion rotatably supported by a planetary carrier and of two central gears, a second planetary gear with three members .consisting of at least one planet pinion rotatably supported by a planet carrier and of two central gears, a driving member drivingly connected with one of the three members of said first planetary gear, a power transmission line connecting a second one of the three members of said first planetary gear with a first one of the three members of said second planetary gear, a driven member drivingly connected with a second one of the three members of said second planetary gear, a brake for the third member of said first planetary gear, a first clutch for locking said first planetary gear in itself, a one-way brake between the third member of said first planetary gear and said relatively fixed part to enable a drive of said last-mentioned third member in only one direction of rotation, a second brake for the planet carrier of said second planetary gear, a second power transmission line includ-ing another clutch between the third one of the three members of said first planetary gear and the third one of the three members of said second planetary gear, and a one-way clutch intermediate said first power transmission line and said driving member to enable a drive of the first member of said second planetary gear in only one direction of rotation with respect to the first member of said first planetary gear.

References Cited in the file of this patent UNITED STATES PATENTS 2,351,213 lames June 13, 1944 2,414,359 Carnagua et al Jan. 14, 1947 2,546,378 Winther Mar. 27, 1951 2,645,137 Roche July 14, 1953 FOREIGN PATENTS 387,623 France Ian. 14, 1947 602,497 Great Britain May 27, 1948 

